JP2958621B2 - Fluid torque converter - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid torque converter in a power transmission system between a drive source and a driven unit, including a pump impeller, a turbine impeller, and a stator impeller. Are disposed rotatably relative to each other about a common axis of rotation and are axially supported by each other by axial support means, a pump impeller close to the driven unit, and a turbine impeller far from the driven unit, A stator impeller provided near the shaft between the pump impeller and the turbine impeller in the axial direction forms an annular primary circuit space inside the hydraulic space, and a pump impeller inside the annular primary circuit space. And a turbine blade and a stator blade, wherein the pump impeller is drive-coupled to a drive source,
The turbine impeller can be coupled to the driven unit by a coupling shaft surrounded by the stator impeller and the pump impeller, and the support tube surrounding the coupling shaft allows the stator impeller to rotate around the rotating shaft via a one-way clutch. A one-way clutch that can be supported against rotation in one rotation direction and has a one-way clutch that transmits torque by engaging the support tube, and an outer clamping wheel that is coupled to the stator hub and transmits torque. Having a tightening body between the inner tightening wheel and the outer tightening wheel in the radial direction,
A working fluid is formed between the stator hub and the support tube, wherein a radial stator impeller support structure surrounding the one-way clutch together, the hydraulic space serves to transmit torque inside the annular primary circuit space A hydraulically operable direct coupling clutch is provided in the torque transmission path between the turbine impeller and the pump impeller, which serves to cool the working fluid and sometimes operates the direct coupling clutch. A working fluid secondary circuit is provided, which is connected to an external working fluid circulation via a conduit partly extending along the coupling axis, the secondary circuit comprising:
The present invention relates to a device including a path portion passing through a stator impeller support structure.

[0002]

2. Description of the Related Art Such a fluid torque converter is known, for example, from German Patent Publication No. 34 47 940.

In a known embodiment, a portion of the secondary circuit passing through the stator impeller support structure is formed between an outer clamping wheel and an inner clamping wheel to form an annular space for receiving a clamping body. It extends to the turbine impeller side support and cover plate,
The support / cover plate is supported by a turbine impeller hub in the axial direction via a turbine impeller-side thrust bearing.

Reference should also be made to EP-A-125 428 as prior art.

[0005] It is also known to extend this path portion inside the support tube. Due to the various design structures of the torque converter, various paths are required to flow the working fluid of the secondary circuit.

[0006]

SUMMARY OF THE INVENTION It is an object of the present invention to facilitate the design of the guide of the working fluid for different designs of the torque converter, on the one hand to enable a quick response of the direct coupling clutch and, on the other hand, to provide a sufficient response. The purpose of the present invention is to show a path in a stator impeller support structure that enables a flow path cross section that allows a cooling flow.

[0007]

According to the present invention, there is provided, in the above-described secondary circuit, a tightening wheel of a one-way clutch for supporting a stator impeller outside a main flow path. A torque converter characterized in that a bypass penetrating through the portion is formed.

A particular advantage of the present invention in that the through-flow channel is routed is that the working fluid of the secondary circuit can be prevented from passing through the gap between the inner and outer clamping wheels. That is, when the working fluid of the secondary circuit is passed through this gap, the response behavior of the tightening body is affected. For example, when the co-rotating operation of the stator impeller shifts to the stopping operation of the stator impeller, the tightening body does not move. It has been found that the system may shift to the tightening state with a delay in a controlled manner.

[0009] The through-passages are preferably arranged in a ring on each of the one or more clamping wheels, the individual through-passes being able to be implemented with a small cross section, thus significantly increasing the radial dimensions of the clamping wheels. Structural strength is maintained in the range of the through-passage without performing.

[0010]

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the case where the through-path extends to the radially outer clamping wheel, the through-path is on the turbine impeller side, and the thrust bearing is disposed between the outer clamping wheel and the turbine impeller. It can be poured radially outward into the annular primary circuit space.

The turbine wheel side thrust bearing is a radially outer clamping wheel, and may be supported by a supporting and covering ring which substantially covers a gap between the outer and inner clamping wheels. it can. The supporting and covering wheel must be rotatable with respect to the radially inner clamping wheel in order not to disturb the behavior of the one-way clutch.

In order to provide a secondary circuit flow path in the outer clamping wheel between the shaft area and the pump impeller-side outlet of the through passage, the pump impeller side supported by at least one of the stator hub and the outer clamping wheel. The radial passage system formed between the cover and the support plate is filled with the through passage of the outer fastening ring on the pump impeller side, and the pump impeller is disposed between the cover and the support plate and the pump impeller. It is possible to accommodate side thrust bearings. This cover and support plate complements the cover and support wheel and can substantially protect the gap between the two tightening wheels on the turbine impeller side from the influence of the flow, and can act on the tightening body. No uncontrolled effects of the fluid occur.

By the means described above, the pump impeller-side thrust bearing can be made substantially dense with respect to the flow without impairing the flow through the stator impeller support structure. In this way, it is possible to prevent the working fluid of the secondary circuit from being sucked in the primary circuit space via the pump impeller-side thrust bearing.

The through-path of the radially outer clamping wheel can be connected on the pump impeller side by means of a radiation channel system to an associated conduit which extends along the coupling shaft and the support tube.

[0015] The flow through the gap between both clamping wheels can be interrupted, as already mentioned. When the one-way clutch is effective, the disconnection does not affect the tightening action of the tightening body, especially its response action, and a very small amount of working fluid required for lubricating the tightening body is removed. It can be chosen so that it can only flow into the gap.

When the through passage penetrates the radially inner clamping wheel, the pump impeller-side outlet is provided radially inward of the pump impeller-side thrust bearing, and the turbine impeller-side outlet of the through passage is on the turbine impeller side. It can be provided radially inside the thrust bearing.

Such a solution, which can be applied in conjunction with the provision of one or more alternative through-passages in the radially outer clamping wheel, still provides a pump impeller-side thrust bearing, while the pump impeller only. It is possible for the vehicle-side thrust bearing to be substantially impervious to fluid in the radial direction.

Even if one or more through-passages are provided in the radially inner clamping wheel, the air gap between the radially outer and the radially inner clamping wheel is still substantially restricted for fluid flow. Can be shut off.

In parallel with one or more of the through-paths of at least one of the inner clamping wheel and the outer clamping wheel, another parallel path is provided in the torque transmitting means between the radial inner clamping wheel and the support tube. It can also be provided. This parallel path has already been used in the past. However, it has been found that this parallel path alone is not sufficient for the secondary circuit on the one hand to ensure a quick response of the direct coupling clutch and on the other hand to ensure efficient heat removal from the torque converter.

The outlet of the at least one through passage on the pump impeller side can be connected, for example, to a conduit provided between the support pipe and an extension pipe projecting toward the driven unit of the pump impeller. .

In the fluid torque converter, for example, a conduit provided between the support pipe and the extension pipe of the pump impeller includes:
It is controlled so that it can be put under pressure to connect the direct coupling clutch. On the other hand, a conduit running inside the coupling shaft can be put under pressure to open the direct coupling and to maintain the secondary circuit.

It should be noted that, in a series of torque converter constructions, the gap between the coupling shaft and the support tube is basically also used as a conduit, for example, the support tube and the extension tube of the pump impeller. Can be provided parallel to the conduit between them, or can be provided parallel to the bore of the coupling axis. On the other hand, in some cases, it may also be necessary to provide an additional thrust bearing between the support tube and the coupling shaft near the stator impeller support structure, for example in the form of a non-ferrous metal bearing shell. In this case, the annular space between the support tube and the connecting shaft is used only to a limited extent as a conduit or not at all. In such an embodiment, it has been found to be particularly advantageous to provide one or more through-holes according to the invention in one or the other clamping wheel.

The design of the fluid torque converter according to the invention is also of particular interest in the case of converter structures in which the direct coupling can be slid by pressure control, in which case the frictional output of the direct coupling is lost due to friction. Occurs and can be discharged through a secondary circuit.

Preventing the working fluid from flowing through the gap between the two tightening wheels also prevents the axial force applied to the tightening body between the tightening wheels if the cross section is designed appropriately. That is, the possibility that the tightening body is frictionally pressed by the pump impeller side cover and support plate to cause wear is avoided.

[0025]

An embodiment of the present invention will be described with reference to the accompanying drawings. The converter housing shown in FIG. 1 is generally designated by the numeral 10 and consists of two parts 12,14. The two parts are tightly connected to one another at 16 and are, for example, welded. The shaft end 18 welded to the converter housing part 14 is inserted into a bearing hole provided at the opposite end of the internal combustion engine crankshaft.

Furthermore, a threaded bush 20 for coupling to the one-way clutch is provided on the converter housing part 14, and the one-way clutch itself can be mounted on a crankshaft (not shown). Converter housing 10 surrounds hydraulic space 22. A pump impeller 24, a turbine impeller 26, and a stator impeller 28 are arranged inside the hydraulic space 22.

The pump impeller 24 is formed by the converter housing portion 12, the pump blade 30, and the inner shell wall 32, and the turbine impeller 26 is formed by the outer shell wall 34, the turbine blade 36, and the inner shell wall 38.
And is formed by.

The stator impeller 28 is formed by a stator hub 40, a stator blade 42, and an inner shell wall 44. The pump impeller 24 is rotatably supported in the crankshaft (not shown) on the one hand via the shaft end 18 and on the other hand in a fixed member by an extension tube 46, for example in the transmission case of a transmission provided downstream of the converter. I have.

The coupling shaft 48 inside the converter housing 10
The left end (not shown) of FIG. 1 is rotatably mounted in the converter housing, and the right end (not shown) is introduced into the transmission to drive the input shaft or gear of the transmission. .

A turbine hub 52 rotatably supported by a pair of teeth 50 on a coupling shaft 48 carries the turbine wheel 26 via a shell wall 34 and is axially supported by a thrust bearing 104 in a portion of the converter housing. Supported by 14. A clutch plate guide 54 is riveted to the turbine hub 52, and a clutch plate 56 having a torsional vibration damper 58 is provided.
Are slidably guided by this guide.

The clutch plate 56 is embodied with a friction coating 60 that frictionally engages a friction surface 62 of the housing portion 14.

A support tube 64 received between the extension tube 46 of the pump impeller 24 and the coupling shaft 48 is supported by a transmission case (not shown) with torsional rigidity, and has an additional bearing shell 66.
Through which the coupling shaft 48 is supported.

The stator hub 40 is supported by a support tube 64 via a one-way clutch 68. The one-way clutch 68 includes a radial inner clamping wheel 70 that is supported in torsional rigidity by a support tube 64 via a pair of teeth 72, an outer clamping wheel 74 that is cast into the stator hub 40, and both clamping wheels. 70, 74 and a clamping body 76 in a gap 78.

The stator hub 40 is supported by a pump impeller-side thrust bearing 80 on the pump impeller 24 side, and is supported by a turbine impeller-side thrust bearing 82 on the turbine hub 52 side.

FIG. 2, which shows an enlarged view of the one-way clutch 68, only shows the two thrust bearings 80, 82 schematically. The thrust bearing 82 acts on the supporting and covering wheel 84 fixed to the outer tightening wheel 74. Support and cover ring 84 is an inner tightening ring
It has a radial running clearance for 70.

On the pump impeller side, a supporting and covering plate 86 is fixed to the outer tightening wheel 74, and this plate abuts on the stator hub 40 at reference numeral 88, and has a running clearance with respect to the inner tightening wheel 70. Having. A pump impeller-side thrust bearing 80 abuts on the pump impeller side of the supporting and covering plate 86, and a passage system 90 is provided substantially radially on the stator and impeller side of the supporting and covering plate 86.

An annular space 92 between the support pipe 64 and the extension pipe 46 of the pump impeller is a conduit section connected to the circulation section of the secondary circuit via a switching valve means, and this circulation section is formed by a gear pump. And is supported by, for example, a transmission case. A second conduit section 94 flowing in the opposite direction is configured, for example, as a central bore inside the coupling shaft 48.

The working fluid filled in the hydraulic space 22 includes a pump impeller 24, a turbine impeller 26, and a stator impeller 28.
The annular annular space 96 is also filled in the range of the blade row. The working fluid inside the annular annular space 96 serves to transmit torque from the pump impeller 24 to the turbine impeller 26, and thus from the crankshaft of the internal combustion engine provided at the front stage to the transmission connected to the coupling shaft 48. And help to transmit torque.

When the rotational speed is in the low rotational speed range, the direct coupling clutch 57 is open, slippage occurs between the pump impeller 24 and the turbine impeller 26, and in the primary circuit 98 of the working fluid, an annular annular space 96 is formed.
Heat is lost inside the

The stator hub 40 and the one-way clutch 68 form a stator impeller support structure 100. A large number of through paths 102 are arranged on the outer peripheral surface of the radially outer tightening wheel 74. Another fluid path through the stator impeller support structure 100 is formed in the area of the tooth pair 72.

The conduit section 94 of the secondary circuit is connected to the pressure side of a circulating section (not shown), for example to the pressure side of a gear pump, when the direct coupling clutch 57 is to be opened in the low rotational speed range. The working fluid flows into the hydraulic space 22 via the passages s1-s2-s3-s4-s5, and the passage s6-s7-s8-s9-s10-s
It can return to the low-pressure side of the circulation section via 11 again.

Next to this, between s6 and s10 (particularly FIG.
), There is a bypass via the through passage 102 and the radial passage system 90. In the bypass s6-102-90-s10, only a slight pressure drop occurs. The void 78 does not flow through and is lubricated with at most a small amount of working fluid.

The pump impeller-side thrust bearing 80 is substantially tightly closed to the flow, so that no flow-through occurs here. In particular, the large cross-section of the bypass s6-102-90-s10 allows for strong flow in the secondary circuit, thus allowing constant cooling of the working fluid in the primary circuit 98, while the direct coupling 57 remains open.

When the direct clutch 57 is to be closed, the annular space 92 is connected to the pressure side of the circulating section by a switching operation at the valve of the circulating section. Then, the pressure of the working fluid is in the path s11-s10-s9
It passes through −s8−s7−s6 and reaches the clutch plate 56 via the bypass s10−90−102−s6. The flow through this path is, for example, due to the pressure on the right side of the clutch plate 56,
This continues until 57 contacts the friction surface 62. Clutch plate 56
Pressure build-up can be done very quickly by bypass s10-90-102-s6.

Since the passage of the fluid is substantially blocked by the thrust bearing 80, the primary circuit 98 of the pump impeller 24 is
When the working fluid is circulated therein, the working fluid is not substantially sucked from the secondary circuit via the thrust bearing 80.

FIGS. 3 and 4 show a variant of FIG. Similar parts have the same reference numerals as in FIG.

The difference from the embodiment of FIG. 1 is that the one-way clutch is used.
It is only in the range of 68A and this is indicated by reference to FIG.

In the embodiment shown in FIGS. 3 and 4, a large number of through passages 102A provided on the peripheral surface penetrate the radially inner tightening wheel 70A. In addition, in this case, another flow path is formed in the stator impeller support structure 100A in the range of the tooth row 72A. The arrangement of the turbine impeller-side thrust bearing 82A and the supporting and covering wheel 84A is the same as that of FIG. 1 or FIG.

On the pump impeller side, a radially outer clamping wheel 74 is provided.
A support and cover plate 86A is fixed to A, and this plate has a running clearance with respect to the radially inner clamping wheel 70A. The pump impeller-side thrust bearing 80A abuts on the pump impeller side of the support / cover plate 86A. The flow of the working fluid in the gap 78A between the two clamping wheels 70A and 74A is substantially prevented by the turbine impeller-side support and cover wheel 84A and the pump impeller-side support and cover plate 86A.

In the embodiment of FIGS. 3 and 4, the conduit section 94A of the secondary circuit is also connected to the pressure side of a circulating section (not shown) when the direct coupling clutch 57A is to be opened in the low rotational speed range. . The working fluid enters the hydraulic space 22A via the flow paths s1A-s2A-s3A-s4A-s5A, and passes through the paths s6A-s7A-s8A-s9A-s10A-s1.
After 1A, it can be recirculated to the low-pressure side of the circulation section via the bypass s6A-s7A-102A-s10A-s11A.

The pump impeller-side thrust bearing 80A is substantially shut off from the flow substantially, so that the working fluid is not sucked into the primary circuit 98A from the secondary flow path via the thrust bearing 80A.

To close the direct coupling clutch 57A, the annular space 92A is connected to the pressure side of the circulating section by switching at the circulating section. Then, the pressure of the circulation part is the path s11A-s10A-s9A-s
Via 8A-s7A-s6A, at the same time bypass s10A-102A-s8A-s7A
-s6A is applied to the right side of the clutch plate 56A. The subsequent course is the same as that of the embodiment of FIGS.
It is not described in detail for this reason.

FIGS. 5 and 6 show another variant of FIG. 1, which corresponds to the embodiment of FIGS. 1 and 2 but additionally has the structure of FIGS. 102. Similar components are again provided with the same reference numerals as in FIGS.

The through passage of the fastening wheel 74B is designated 103B in this case and intersects with the connecting passage between the stator hub 40B and the outer fastening wheel 74B like a roof.

The secondary circuit in this case extends through the stator impeller support structure 100B in all operating states in a total of three paths. That is, path s10B-s9B-s8B-s7B-s6B path s10B-102B-s8B-s7B-s6B path s10B-90B-103B-s6B and vice versa.

[0056]

A particular advantage of the present invention in that it guides the through flow path is that the working fluid of the secondary circuit can be prevented from passing through the gap between the inner and outer clamping wheels. . That is, when the working fluid of the secondary circuit is passed through this gap, the response behavior of the tightening body is affected. For example, when the co-rotating operation of the stator impeller shifts to the stopping operation of the stator impeller, the tightening body does not move. It has been found that the system may shift to the tightening state with a delay in a controlled manner.

The through-passes are preferably arranged in a ring on each of the one or more clamping wheels, and the individual through-passes can be implemented with a small cross-section, thus significantly increasing the radial dimensions of the clamping wheels. Structural strength is maintained in the range of the through-pass without performing.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view including an axis of a first embodiment of the present invention.

FIG. 2 is an enlarged partial view of FIG. 1;

FIG. 3 is a cross-sectional view including an axis of a second embodiment of the present invention.

FIG. 4 is an enlarged partial view of FIG. 3;

FIG. 5 is a sectional view including an axis of a third embodiment of the present invention.

FIG. 6 is an enlarged partial view of FIG. 5;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Converter housing 12 Converter housing part 14 Converter housing part 18 Shaft end 20 Screw bush 22 Hydraulic space 24 Pump impeller 26 Turbine impeller 28 Stator impeller 30 Pump impeller 32 Inner shell wall 36 Turbine blade 38 Inner shell wall 40 Stator hub 42 Stator blade 44 Inner shell wall 46 Extension tube 48 Coupling shaft 50 Tooth row pair 52 Turbine hub 54 Clutch plate guide 56 Clutch plate 57 Direct coupling clutch 58 Torsional vibration damper 60 Friction film 62 Friction surface 64 Support tube 68 One-way clutch 70 Inner fastening Ring 74 Outer clamping wheel 76 Clamping body 78 Air gap 80 Thrust bearing 82 Thrust bearing 84 Supporting / covering ring 86 Covering / supporting plate 90 Radiation passage system 92 Conduit passage 96 Circular primary circuit space 92 Conduit passage 94 Conduit passage 96 One ring Circuit space 100 stator impeller support structure 102 through passage 104 axially supporting means s1~s11 working fluid secondary circuit s6~s10 path portion

──────────────────────────────────────────────────続 き Continued from the front page (56) References JP-A-57-184750 (JP, A) JP-A-54-172166 (JP, U) JP-A-61-135052 (JP, U) (58) Investigation Field (Int.Cl. ⁶ , DB name) F16H 41/24-41/30 F16H 45/02

Claims (17)

(57) [Claims] 1. A fluid torque converter in a power transmission system between a drive source and a driven unit, comprising a pump impeller (2).
4), a turbine impeller (26) and a stator impeller (28), which are arranged rotatably relative to each other about a common axis of rotation and have axial support means (80, 82, 1).
04) are axially supported by each other, the pump impeller (24) close to the driven unit, the turbine impeller (26) far from the driven unit, and the pump impeller (24) and the turbine impeller in the axial direction. A stator impeller (28) provided in the vicinity of the shaft with (26) forms an annular primary circuit space (96) inside the hydraulic space (22), and an annular primary circuit space (96). Inside the pump blade (30), the turbine blade (36) and the stator blade (4).
2), wherein the pump impeller (24) is drivingly connected to a driving source, and the turbine impeller (24) is surrounded by a coupling shaft (48) surrounded by the stator impeller (28) and the pump impeller (24). 2
6) can be connected to the driven unit, and the stator impeller (28) is supported by the support tube (64) surrounding the connection shaft (48) via the one-way clutch (68) in one rotation direction around the rotation shaft. A one-way clutch (68) is coupled to the inner clamping wheel (70) that engages the support tube (64) to transmit torque and the stator hub (40). A one-way clutch, comprising: an outer tightening wheel (74) for transmitting torque through a shaft; and a tightening body (76) between the inner tightening wheel (70) and the outer tightening wheel (74) in the radial direction. A radial stator impeller support structure (100) that surrounds (68) together has a stator hub (4).
0) and a support tube (64), wherein the hydraulic space (22) contains a working fluid that serves to transmit torque within the annular primary circuit space (96), A hydraulically operable direct-coupled clutch (57) is provided in a torque transmission path (54-62) between the car (26) and the pump impeller (24) to help cool the working fluid and A working fluid secondary circuit (s1 to s11) is provided, possibly to operate the direct coupling clutch (57), this circuit comprising a conduit (92) extending partly along the coupling axis (48). , 94), the secondary circuit (s1 to s11) includes a path portion (s6 to s10) passing through the stator impeller support structure (100). In the above secondary circuit , Outside the main channel, a torque converter, wherein a bypass passing through the portion of the tightening ring of the one-way clutch supporting the stator impeller (28) is formed. 2. The torque converter according to claim 1, wherein the bypass is a through passage (102) passing through the outer tightening wheel (74). 3. The bypass according to claim 1, wherein the bypass is an inner clamping wheel (70A).
The torque converter according to claim 1, wherein the torque converter is a through path (102A) penetrating through. 4. The bypass according to claim 1, wherein the bypass is an outer clamping wheel (74B).
(103B) and inner clamping ring (70B)
2. A torque converter according to claim 1, wherein the torque converter is a through path (102B) penetrating through. 5. A through-passage (102) passing through a radially outer tightening wheel (74) on the turbine impeller side.
The torque converter according to claim 1, characterized in that the thrust bearing (82) arranged between the (74) and the turbine impeller (26) opens radially outside of the thrust bearing (82) into the annular primary circuit space. . 6. A turbine impeller side thrust bearing (82).
Is supported and covered with a radially outer fastening ring (74) and a cover ring (84)
Supported and covered by a gap (78) between the outer clamping ring (74) and the inner clamping ring (70).
The torque converter according to claim 5, wherein a cover is provided. 7. A passage (102) passing through the outer clamping wheel (74) opens on the pump impeller side into a radiation passage system (90), which passage system comprises a stator hub (40) and an outer clamping wheel. (74) and a cover / support plate (86) attached to the stator hub (40) on the pump impeller side. The cover / support plate (86) and the pump impeller are formed. The torque converter according to any one of claims 5 and 6, wherein a pump impeller-side thrust bearing (80) is accommodated between the thrust bearing (80) and the thrust bearing (80). 8. A pump impeller side thrust bearing (80).
Is connected to the attached conduit (92) and the annular primary circuit space (9).
8. The communication with (6) is interrupted.
The torque converter according to 1. 9. The method according to claim 1, wherein the flow through the gap between the two clamping wheels is completely obstructed. Torque converter. 10. When the through-passage (102A) passes through the radially inner fastening ring (70A), the through-passage (102A) is provided.
The pump impeller-side outlet of A) is located radially inside the pump impeller-side thrust bearing (80A), and the turbine impeller-side outlet of the through passage (102A) is located radially of the turbine impeller-side thrust bearing (82A). The torque converter according to claim 1, wherein the torque converter is located inside. 11. A thrust bearing (80) on a pump impeller side.
The torque converter according to claim 10, wherein A) is impervious to fluid in the radial direction. 12. A thrust bearing (82) for a turbine impeller.
A) characterized in that A) passes through a fluid.
The torque converter according to 1. 13. The method according to claim 9, wherein the gap between the radially outer clamping wheel (74A) and the radially inner clamping wheel (70A) is blocked against fluid flow. The torque converter according to claim 1. 14. A support tube (64) and a one-way clutch (6).
8) At least one through passage (102) is provided in parallel with the auxiliary through passage (72) formed by the torque transmitting engagement means (72) with the inner tightening wheel (70). The torque converter according to any one of claims 1 to 13, wherein: 15. A support pipe (64) and a pump impeller (2).
A conduit (92) is formed between the extension pipe (46) and the extension pipe (46) projecting in the direction of the driven unit (4). The pump impeller-side outlet of at least one through-path (102) is connected to the conduit. The torque converter according to any one of claims 1 to 14, wherein: 16. A support pipe (64) and a pump impeller (2).
4) The conduit (9) formed between the pipe and the extension pipe (46).
16. The torque converter according to claim 15, wherein 2) can be put under pressure for connecting a direct coupling clutch (57). 17. A conduit (94) extending inside the coupling shaft (48) is under pressure to open the direct coupling (57) and to maintain the secondary circuit (s1-s11). 17. The torque converter according to claim 1, wherein the torque converter can be placed.